Ball type continuously variable transmission/infinitely variable transmission

ABSTRACT

A variable transmission includes an input shaft, a planetary gear set drivingly engaged with a variator comprising, a variator carrier assembly, a first ring assembly, and a second ring assembly; and the output shaft, arranged with various combinations of brakes and clutches to produce transmissions with continuously variable or infinitely variable torque output ratios.

CROSS-REFERENCE

This application is filed pursuant to 35 U.S.C. §371 as a United States National Phase Application of International Application No. PCT/US2013/058616, filed Sep. 6, 2013, which application claims the benefit of U.S. Provisional Application No. 61/782,924, filed Mar. 14, 2013, and U.S. Provisional Application No. 61/698,005, filed Sep. 7, 2012, which are incorporated herein by reference in their entirety.

BACKGROUND OF THE INVENTION

Automatic and manual transmissions are commonly used on automobile vehicles. Those transmissions are becoming more and more complicated since the engine speed has to be more precisely controlled to limit the fuel consumption and the emissions of cars. This finer control of the engine speed in usual transmissions can only be done by adding more discrete step ratio gears and increasing the overall complexity and cost. Consequently, 6-speed manual transmissions then become more frequently used as are 8 or 9 speed automatic transmissions.

SUMMARY OF THE INVENTION

Provided herein is a variable transmission comprising; a power input shaft; a planetary gear set mechanically coupled to the power input shaft, a variator comprising, a variator carrier assembly, a first ring assembly, and a second ring assembly; and various combinations of brakes and clutches.

In any of the embodiments disclosed herein the variable transmission may be a continuously variable transmission

In some embodiments, the variable transmission comprises a variator having a continuously variable mode, an infinitely variable mode or a combination thereof.

In some embodiments the variable transmission can provide a reverse function, a standstill function and a low speed function.

In some embodiments, the transition between continuously variable transmission mode and infinitely variable transmission mode is accomplished by simultaneously releasing one of the brakes and applying the other brake.

In some embodiments, the transition between continuously variable transmission mode and infinitely variable transmission mode is accomplished by releasing the clutch and engaging the brake.

In some embodiments, the variator is able to continuously change its torque ratios in both the continuously variable mode and infinitely variable mode to provide the best ratio achievable for the engine to optimize performance or fuel consumption.

Provided herein is a variable transmission comprising: an input shaft; a planetary gear set, wherein a carrier of the planetary gear set is drivingly engaged with the input shaft; a first brake mechanically coupled to a ring gear of the planetary gear set; a variator comprising a variator carrier assembly, a first ring assembly, and a second ring assembly, wherein the variator carrier assembly is mechanically coupled to the ring gear of the planetary gear set; and a second brake is mechanically coupled to a sun gear of the planetary gear set and to the first ring assembly of the variator, and wherein the second ring assembly of the variator assembly is drivingly engaged to the output of the variable transmission.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode. In some embodiments, when the first brake is engaged and the second brake is disengaged, the ring gear of the planetary gear set and the variator carrier assembly are held fixed, thereby engaging a continuously variable mode. In some embodiments, power passes through the sun gear of the planetary gear set to the first ring assembly when the transmission is in continuously variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the sun gear of the planetary gear set and the first ring assembly are held fixed, thereby engaging an infinitely variable mode. In some embodiments, power passes through the ring gear of the planetary gear set to variator carrier assembly in the infinitely variable mode. In some embodiments, in the infinitely variable mode, the variator provides a reverse function, a standstill function and a low speed function.

In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 5.

In some embodiments, a gearbox is added so that the gap previously present might be completely covered without engine speed adjustment. The gearbox allows to continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the variable transmission, the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing a spread between the max forward and reverse speeds at the variable transmission output of the embodiment.

Provided herein is a variable transmission comprising: an input shaft; a planetary gear set, wherein a ring gear of the planetary gear set is drivingly engaged with the input shaft; a variator comprising a variator carrier assembly, a first ring assembly, and a second ring assembly; a planetary gear carrier of the planetary gear set coupled to a first brake and to the second ring assembly; and a sun gear of the planetary gear set coupled to a second brake and the variator carrier assembly, and wherein the second ring assembly of the variator is drivingly engaged to the output of the variable transmission.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the sun gear of the planetary gear set is fixed together with the variator carrier assembly to engage a continuously variable mode. In some embodiments, input power passes through the ring gear of the planetary gear set to the first ring assembly when the transmission is in continuously variable mode.

In some embodiments, when the first brake is engaged and the second brake is disengaged, the first ring assembly of the variator and the planetary gear carrier are held fixed, to engage an infinitely variable mode. In some embodiments, in the infinitely variable mode, the variator provides a reverse function, a standstill function, and a low speed function.

In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode have overlapping rotation speeds of the second ring assembly (or transmission output). In some embodiments, rotation speed range of the infinitely variable mode is wider than the rotation speed in the continuously variable mode. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 7.

Provided herein is a variable transmission comprising: an input shaft; a variator comprising a first ring assembly, a second ring assembly, and a carrier assembly; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, a ring gear drivingly engaged with the variator carrier assembly, and one or more planet gears on a planet carrier, the planet gears disposed in mechanical engagement between the sun gear and the ring gear; a first brake coupled to the ring gear and configured to hold the ring gear fixed when the first brake is engaged; and a second brake coupled to the planet carrier and the first ring assembly, and configured to hold the planet carrier fixed when the second brake is engaged; and wherein the second ring assembly is drivingly engaged with the output of the variable transmission.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode.

In some embodiments, when the first brake is engaged and the second brake is disengaged, the ring gear and the variator carrier assembly are fixed to engage a continuously variable mode. In some embodiments, input power passes through the planetary carrier to the first ring assembly when the transmission is in the continuously variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the planet carrier and the first ring assembly are held fixed by the second brake to engage an infinitely variable mode. In some embodiments, power passes through the ring gear of the planetary gear set, to the variator carrier assembly when the transmission is in the infinitely variable mode. In some embodiments, in the infinitely variable mode the variator provided a reverse function, a standstill function and a low speed function.

In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode provide overlapping rotation speeds of the second ring assembly. In some embodiments, the continuously variable mode and infinitely variable mode have lower rotation speeds of the second ring assembly than a rotation speed of the input shaft. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 9.

Provided herein is a variable transmission comprising: an input shaft, a variator comprising a first ring assembly, a second ring assembly, and a carrier assembly, wherein the second ring assembly is drivingly engaged to an output of the variable transmission; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, a ring gear drivingly engaged with the second ring assembly, and one or more planet gears on a planet carrier, the planet gears disposed in mechanical engagement between the sun gear and the ring gear; a first brake coupled to the first ring assembly and configured to hold the ring gear of the planetary gear set and the first ring assembly fixed when the first brake is engaged; and a second brake coupled to the planet carrier and the variator carrier assembly, and configured to hold the planet carrier and the variator carrier assembly fixed when the second brake is engaged.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the planet carrier and the variator carrier assembly are held fixed to engage a continuously variable mode. In some embodiments, power passes through the planetary gear set ring gear and goes to the first ring assembly when the transmission is in the continuously variable mode.

In some embodiments, when the first brake is engaged and the second brake is disengaged, the ring gear and the first ring assembly are held fixed to engage an infinitely variable mode. In some embodiments, power passes through the planet carrier to the variator carrier assembly when the transmission is in the infinitely variable mode.

In some embodiments, in the infinitely variable mode the variator provides a reverse function, a standstill function and a low speed function. In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the CVT input from the engine is as shown in FIG. 11.

Provided herein is a variable transmission comprising: an input shaft; a clutch comprising a first clutch member coupled to the input shaft and a second clutch member; a variator comprising, a carrier assembly, a first ring assembly having the second clutch member formed theron, and a second ring assembly, and wherein the second ring assembly is drivingly engaged to an output of the variable transmission; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, one or more planet gears on a planet carrier, wherein the planet carrier is drivingly engaged with the variator carrier, and wherein a ring gear of the planetary gear set is held fixed; and a first brake coupled to the first ring assembly configured to hold the first ring assembly fixed when the first brake is engaged, wherein the first ring assembly is drivingly engaged with the input shaft when the first clutch member engages the second clutch member.

In some embodiments, the variable transmission comprises a combined continuously variable/infinitely variable mode (CVP/IVP mode), or an infinitely variable mode.

In some embodiments, when the clutch is engaged, both the first ring assembly and the variator carrier are driven in order to engage the combined continuously variable/infinitely variable mode (CVP/IVP mode). In some embodiments, the variable transmission in the combined continuously variable/infinitely variable mode generates rotation speeds of the second ring assembly between speeds generated in a continuously variable mode and an infinitely variable mode.

In some embodiments, when the first ring assembly is held fixed with the first brake and the clutch is disengaged, the infinitely variable mode is engaged. In some embodiments, the power passes through the planet carrier of the planetary gear set and to the variator carrier in the infinitely variable mode. In some embodiments, the variator provides a reverse function, a standstill function and a low speed function in the infinitely variable mode.

In some embodiments, a transition between the continuously variable/infinitely variable mode (CVP/IVP mode) and the infinitely variable (IVP) mode is accomplished by engaging/disengaging the clutch and engaging/disengaging the first brake. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the CVP/IVP mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the CVP/IVP mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 13. In some embodiments, a gearbox is added so that the gap previously present might be completely covered without engine speed adjustment. The gearbox facilitates continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the variable transmission (by selecting the ratio of the variator), the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing the spread of speeds between the forward maximum speed and maximum reverse speed of the output of the embodiment.

Provided herein is a vehicle driveline comprising an engine, a variable transmission of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein, and a vehicle output. In some embodiments, the vehicle output comprises a wheel differential and one or more wheels of a vehicle. In some embodiments, the vehicle output comprises a wheel differential and a drive axle. In some embodiments, the dampener is disposed between the engine and the variable transmission. In some embodiments, the dampener comprises at least one torsional spring.

Provided herein is a method comprising providing a variable transmission of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein.

Provided herein is a method comprising providing a vehicle driveline of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein.

INCORPORATION BY REFERENCE

All publications, patents, and patent applications mentioned in this specification are herein incorporated by reference to the same extent as if each individual publication, patent, or patent application was specifically and individually indicated to be incorporated by reference.

BRIEF DESCRIPTION OF THE DRAWINGS

The novel features of the invention are set forth with particularity in the appended claims. A better understanding of the features and advantages of the present invention will be obtained by reference to the following detailed description that sets forth illustrative embodiments, in which the principles of the invention are utilized, and the accompanying drawings of which:

FIG. 1 is a side sectional view of a continuously variable planetary (CVP) transmission;

FIG. 2 is a magnified, side sectional view of a ball and ring of the CVP transmission of FIG. 1;

FIG. 3 is a block diagram of a continuously variable transmission (CVT) used in an automobile;

FIG. 4A is a block diagram of a continuously variable transmission (CVT) according to an embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode;

FIG. 4B is a block diagram of a continuously variable transmission (CVT) according to an embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode and an additional gearbox;

FIG. 5 is a graph of a speed diagram of the second (output) ring assembly in FIG. 4 a;

FIG. 6 is a block diagram of a continuously variable transmission (CVT) according to another embodiment of the present disclosure used in an automobile having both a continuously variable CVP mode and an infinitely variable planetary mode;

FIG. 7 is a graph of a speed diagram of the second (output) ring assembly in FIG. 6;

FIG. 8 is a block diagram of a continuously variable transmission CVT according to another embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode;

FIG. 9 is a graph of a speed diagram of the second (output) ring assembly in FIG. 8;

FIG. 10 is a block diagram of a continuously variable transmission (CVT) according to another embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode;

FIG. 11 is a graph of a speed diagram of the second (output) ring assembly in FIG. 10;

FIG. 12A is a block diagram of a continuously variable transmission (CVT) according to another embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode;

FIG. 12B is a block diagram of a continuously variable transmission (CVT) according to another embodiment of the present disclosure used in an automobile having both a continuously variable mode and an infinitely variable mode and an additional gearbox; and

FIG. 13 is a graph of a speed diagram of the second (output) ring assembly in FIG. 12A.

DETAILED DESCRIPTION OF THE INVENTION

Besides the automatic and manual transmissions now commonly used on automobile vehicles, Continuously Variable Transmissions or CVTs have been developed. Those CVTs are of many types: belts with variable pulleys, toroidal, and conical, for non-limiting example. The principle of a CVT is that it enables the engine to run at its most efficient rotation speed by steplessly changing the transmission ratio as a function of the speed of the car and the torque demand (throttle position) of the driver. If needed for example when accelerating, the CVT can also shift to the most optimum ratio providing more power. A CVT can change the ratio from the minimum to the maximum ratio without any interruption of the power transmission, as opposed to the usual transmissions which require an interruption of the power transmission by disengaging to shift from one discrete ratio to engage the next ratio.

A specific use of CVTs is the Infinite Variable Transmission or IVT. Where the CVT is limited to positive speed ratios, the IVT configuration can perform a neutral gear and even reverse ratios steplessly. A CVT can be used as an IVT in some driveline configurations.

Provided herein are configurations based on a ball type CVT, also known as CVP, for continuously variable planetary. Aspects of the CVTs are described in US20040616399 or AU2011224083A1, incorporated herein by reference in their entirety. The type of CVT used herein is composed of a plurality of variator balls, depending on the application, two discs or annular rings each having an engagement portion that engages the variator balls. The engagement portions may be in a conical or toroidal convex or concave surface contact with the variator balls, as input and output. The CVT may include an idler contacting the balls as well as shown on FIG. 1. The variator balls are mounted on axes, themselves held in a cage or carrier allowing changing the ratio by tilting the variator balls' axes. Other types of ball CVTs also exist, like the one produced by Milner but are slightly different. These alternative ball CVTs are additionally contemplated herein. The working principle generally speaking, of a ball-type CVT is shown in FIG. 2.

The CVP itself works with a traction fluid. The lubricant between the ball and the conical rings acts as a solid at high pressure, transferring the power from the first ring assembly, through the variator balls, to the second ring assembly. By tilting the variator balls' axes, the ratio can be changed between input and output. When the axis of each of the variator balls is horizontal the ratio is one, when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio. All the variator balls'axles are tilted at the same time with a mechanism included in the cage.

In a car, the CVT is used to replace traditional transmission and is located between the engine (ICE or internal combustion engine) and the differential as shown on FIG. 3. A torsional dampener (alternatively called a damper) may be introduced between the engine and the CVT to avoid transferring torque peaks and vibrations that could damage the CVT. In some configurations this dampener can be coupled with a clutch for the starting function.

Embodiment transmissions (and a resulting drivelines) are shown in FIGS. 4A, 4B, 6, 8, 10, and 12A, 12B. The central part of these configurations is a variator, such as variator 10 a (also depicted as elements 10 b-e). Such variators may typically comprise the tilting ball type CVPs described above. Such variators 10 a-10 e typically each comprises a first ring assembly, a second ring assembly, and a carrier assembly disposed therebetween. Referring now to FIG. 4a , variator 10 a is shown comprising a first ring assembly 12A, a second ring assembly 11 a, and a carrier assembly 13 a (also referred to as a “variator carrier assembly” or “variator carrier”). The carrier assembly typically includes a plurality of variator balls having tiltable axle shafts as described herein. In some embodiments, the first ring assembly is rotatably disposed in a housing; the first ring assembly comprises a first variator ball engagement surface that is in driving engagement with a plurality of variator balls of the carrier assembly. In some embodiments the first ring assembly may be drivingly engaged with input shaft.

A first variator ball engagement surface is formed in a distal end of the first ring assembly. As meant herein, when describing the ring assemblies of a variator, distal means the portion of the ring assembly closest to the variator balls. In some embodiments, the first variator ball engagement surface is a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls. In some embodiments, the first variator ball engagement surface is in driving engagement with each of the variator balls of the carrier assembly through one of a boundary layer type friction and an elastohydrodynamic film.

The variator carrier assemblies (13 a-e) of some embodiments shown in FIGS. 4A, 4B, 6, 8, 10, and 12A, 12B may be rotatably disposed in the housing and is drivingly engaged with the first ring assembly. In some embodiments, the carrier assembly may comprises an annular arrangement of the plurality of tiltable variator balls each having tiltable ball axle shafts. A cage of the carrier assembly may be configured to be prevented from rotating relative to the housing by a grounding device linked to said ground. In some embodiments, each of the ball axle shafts is adjusted using a cam style tilting mechanism. In some embodiments, each of the ball axle shafts is adjusted using a split carrier axle skewing mechanism.

As depicted in FIGS. 4A, 4B, 6, 8, 10, and 12A, 12B, at least, the second ring assembly is rotatably disposed in the housing. The second ring assembly comprises a second variator ball engagement surface that is in driving engagement with variator balls of the carrier assembly. In some embodiments, the second variator ball engagement surface is formed in a distal end of the second ring assembly. In some embodiments, the second variator ball engagement surface is a conical surface or a concave or convex toroidal surface in contact with or slightly spaced apart from each of the variator balls. In some embodiments, the second variator ball engagement surface is in driving engagement with each of the variator balls of the carrier assembly through one of a boundary layer type friction and an elastohydrodynamic film.

A ball ramp on each side of the variator (depicted as elements 15 a-e) provides the clamping force necessary to transfer the torque. Ball ramps, indicated in FIGS. 4A, 4B, 6, 8, 10, and 12A, 12B by a circle between a pair of vertical lines, making up a first thrust ring on the first ring assembly and a second thrust ring on the second ring assembly are disposed between components of the variable transmission as shown to generate an amount of axial force necessary for proper operation of the variable transmission (i.e. transfer of torque); however, it is understood that the amount of axial force necessary for proper operation may be generated by a clamping mechanism (not shown) or as a load applied during assembling of the variable transmission. Thus, as depicted in FIGS. 4A, 4B, 6, 8, 10, and 12A, 12B, a ball ramp on each side of the variator provides the clamping force necessary to transfer the torque in this embodiment.

Provided herein is a variable transmission comprising; a power input shaft; a planetary gear set mechanically coupled to the power input shaft, a variator comprising, a variator carrier assembly, a first ring assembly, and a second ring assembly; and various combinations of brakes and clutches.

In some embodiments, the variable transmission comprises a variator having a continuously variable mode, an infinitely variable mode or a combination thereof.

In some embodiments the variable transmission can provide a reverse function, a standstill function and a low speed function.

In some embodiments, the transition between continuously variable transmission mode and infinitely variable transmission mode is accomplished by simultaneously releasing one of the brakes and applying the other brake.

In some embodiments, the transition between continuously variable transmission mode and infinitely variable transmission mode is accomplished by releasing the clutch and engaging the brake.

In some embodiments, the variator is able to continuously change its torque ratios in both the continuously variable mode and infinitely variable mode to provide the best ratio achievable for the engine to optimize performance or fuel consumption.

Provided herein is a variable transmission (VT) comprising: an input shaft; a planetary gear set drivingly engaged with the input shaft though its planet carrier; a first brake mechanically coupled to a ring gear of the planetary gear set; a variator comprising a variator carrier assembly, a first ring assembly, and a second ring assembly, the carrier of the variator mechanically coupled to a ring gear of the planetary gear set; and a second brake mechanically coupled to a sun gear of the planetary gear set and to the first ring assembly, a second ring assembly is drivingly engaged with the output of the VT. Such a variable transmission is depicted in the embodiment of FIG. 4A.

FIG. 4A depicts a VT of a particular embodiment of the present invention comprising: an input shaft 1; a planetary gear set 5 a drivingly engaged with the input shaft though its planet carrier 8 a; a first brake 16 mechanically coupled to a ring gear 9 a of the planetary gear set; a variator 10 a (as described elsewhere in this application) comprising a variator carrier assembly 13 a, a set of tilting balls 14 a, a first ring assembly 12 a, and a second ring assembly 11 a, the variator carrier assembly is mechanically coupled to the ring gear 9 a of the planetary gear set 5 a; and a second brake 17 may be mechanically coupled to the sun gear 6 a of the planetary gear set and to the first ring assembly 12 a. The second ring assembly 11 a is drivingly engaged with the output of the VT.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode. In some embodiments when the first brake is engaged and the second brake disengaged, the ring gear of the planetary gear set and a variator carrier assembly (also referred to as a “variator carrier” or “carrier of the variator”) are held fixed, thereby engaging the continuously variable mode. In some embodiments power may pass through the sun gear of the planetary gear set to the first ring assembly when the transmission is in continuously variable mode. For example, in the embodiment of FIG. 4A: when the first brake is engaged and the second brake is disengaged, the ring gear 9 a of the planetary gear set 50 a and variator carrier assembly 13 a are held fixed, thereby engaging a continuously variable mode.

In some embodiments when the second brake is engaged and the first brake is disengaged the sun gear of the planetary gear set and the first ring assembly are held fixed, thereby engaging an infinitely variable mode. In some embodiments, power passes through the ring gear of the planetary gear set to a carrier of the variator in the infinitely variable mode. In some embodiments, in the infinitely variable mode, the variator provides a reverse function, a standstill function, and a low speed function. For example in the embodiment of FIG. 4A, when the second brake is engaged and the first brake is disengaged, the sun gear 6 a of the planetary gear set 5 a and the first ring assembly are held fixed, thereby engaging an infinitely variable mode. In such a mode, power may pass through the ring gear 9 a of the planetary gear set 5 a to the variator carrier assembly 13 a.

In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 5.

In some embodiments, a gearbox is added so that the gap previously present might be completely covered without engine speed adjustment. FIG. 4B shows the embodiment of FIG. 4A with a gearbox 18 added between the CVT and the differential 4. In some embodiments the gearbox allows for continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the CVT (at the variator), the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing the spread between the max reverse speed and the max forward speed of the CVT transmission output of the embodiment.

Provided herein is a variable transmission comprising: an input shaft; a ring gear of the planetary gear set drivingly engaged with the input shaft; a variator comprising a variator carrier assembly, a first ring assembly, and a second ring assembly; a planetary gear carrier coupled to a first brake and to the first ring assembly; and a sun gear coupled to a second brake and a variator carrier; a second ring assembly of the variator drivingly engaged to the output of the VT.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode. In some embodiments, when the second brake is engaged and the first brake is disengaged the sun gear of the planetary gear set is fixed together with the variator carrier assembly to engage a continuously variable mode. An example of such an embodiment is depicted in FIG. 6 and is discussed below.

In some embodiments when the first brake is engaged and the second brake disengaged an input ring assembly (typically the first ring assembly) of the variator and the planetary gear carrier (also referred to as “planet carrier” or “planetary carrier assembly”) is fixed, thereby engaging an infinitely variable mode. In some embodiments, in the infinitely variable mode, the variator provides a reverse function, a standstill function, and a low speed function (forward speed). An example of such an embodiment is depicted in FIG. 6.

In some embodiments, an example of which is depicted in FIG. 6, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In such embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode have overlapping rotation output speeds. For example, in the embodiment depicted in FIG. 6, the continuously variable mode and the infinitely variable mode may have overlapping rotation speeds of the second ring assembly. In some embodiments, a rotation speed range of the infinitely variable mode may be wider than the rotation speed in the continuously variable mode. FIG. 7 shows an exemplary relationship between rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode.

Provided herein is a variable transmission comprising: an input shaft; a variator comprising a first ring assembly, a second ring assembly, and a carrier assembly (also referred to as the “variator carrier assembly”), wherein the second ring assembly is drivingly engaged with the output of the VT ; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, a ring gear drivingly engaged with the variator carrier assembly, and one or more planet gears on a planet carrier (also referred to as a “planetary carrier assembly”), the planet gears disposed in mechanical engagement between the sun gear and the ring gear; a first brake coupled to the ring gear and configured to hold the ring gear fixed when the first brake is engaged; and a second brake coupled to the planet carrier and the first ring assembly, and configured to hold the planet carrier and the first ring assembly fixed when the second brake is engaged. An example of such an embodiment is depicted in FIG. 8.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode.

In some embodiments, when the first brake is engaged and the second brake is disengaged, the ring gear and the variator carrier assembly are both fixed to engage a continuously variable mode. In some embodiments, input power passes through the planetary carrier to the first ring assembly when the transmission is in the continuously variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the planet carrier and the first ring assembly are held fixed by the second brake to engage an infinitely variable mode. In some embodiments, power passes through the ring of the planetary gear set, to the variator carrier when the transmission is in the infinitely variable mode. In some embodiments, in the infinitely variable mode the variator provided a reverse function, a standstill function and a low speed function.

In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.

In some embodiments, the continuously variable mode and infinitely variable mode provide overlapping rotation speeds of the second ring assembly. In some embodiments, the continuously variable mode and infinitely variable mode have lower rotation speeds of the second ring assembly than a rotation speed of the input shaft. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 9.

Provided herein is a variable transmission comprising: a variator comprising a first ring assembly, a second ring assembly drivingly engaged to the output of the VT, and a carrier assembly; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, a ring gear drivingly engaged with the first ring assembly, and one or more planet gears on a planet carrier, the planet gears disposed in mechanical engagement between the sun gear and the ring gear; a first brake coupled to the first ring assembly and configured to hold the ring gear of the planetary gear set and the first ring assembly fixed when the first brake is engaged; and a second brake coupled to the planet carrier and a variator carrier of the carrier assembly, and configured to hold the planet carrier and the variator carrier fixed when the second brake is engaged.

In some embodiments, the variable transmission comprises a continuously variable mode and an infinitely variable mode.

In some embodiments, when the second brake is engaged and the first brake is disengaged, the planetary carrier assembly and the variator carrier are held fixed to engage a continuously variable mode. In some embodiments, power passes through the planetary ring gear and goes to the first ring assembly when the transmission is in the continuously variable mode.

In some embodiments, when the first brake is engaged and the second brake is disengaged, the ring gear and the first ring assembly are held fixed to engage an infinitely variable mode. In some embodiments, power passes through the planetary carrier assembly to the variator carrier assembly when the transmission is in the infinitely variable mode.

In some embodiments, in the infinitely variable mode the variator provided a reverse function, a standstill function and a low speed function. In some embodiments, a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.

In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for the VT.

In some embodiments, the continuously variable mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the continuously variable mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 11.

Provided herein is a variable transmission comprising: an input shaft; a clutch comprising a first clutch member coupled to the input shaft and a second clutch member; a variator comprising a first ring assembly having the second clutch member formed thereon, a second ring assembly drivingly engaged to the output of the VT, and a carrier assembly; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, one or more planet gears on a planet carrier (also referred to as a “planetary carrier assembly”) that is drivingly engaged with the variator carrier assembly, a ring gear, wherein the ring gear of the planetary gear set is held fixed; and a first brake coupled to the first ring assembly configured to hold the first ring assembly fixed when the first brake is engaged, wherein the first ring assembly is drivingly engaged with the input shaft when the first clutch member engages the second clutch member.

In some embodiments, the variable transmission comprises a combined continuously variable/infinitely variable mode (CVP/IVP mode), or an infinitely variable mode.

In some embodiments, when the clutch is engaged, both the first ring assembly and the variator carrier are driven in order to engage the combined continuously variable/infinitely variable mode (CVP/IVP mode). In some embodiments, the variable transmission in the combined continuously variable/infinitely variable mode generates rotation speeds of the second ring assembly between speeds generated in a continuously variable mode and an infinitely variable mode.

In some embodiments, when the first ring assembly is held fixed with the first brake and the clutch is disengaged, the infinitely variable mode is engaged. In some embodiments, the power passes through the planet carrier of the planetary gear set and to the variator carrier in the infinitely variable mode. In some embodiments, the variator provides a reverse function, a standstill function and a low speed function in the infinitely variable mode.

In some embodiments, a transition between the continuously variable/infinitely variable mode (CVP/IVP mode) and the infinitely variable (IVP) mode is accomplished by engaging/disengaging the clutch and engaging/disengaging the brake. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption. In some embodiments, the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for the VT.

In some embodiments, the CVP/IVP mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly. In one embodiment, the gap is compensated by engine speed adjustment. In some embodiments, the relationship of rotation speeds of the second ring assembly in the CVP/IVP mode and the second ring assembly in the infinitely variable mode, and the rotation speed of the input shaft from the engine is as shown in FIG. 13.

In some embodiments, a gearbox is added so that the gap previously present might be completely covered without engine speed adjustment. The gearbox allows continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the CVT, the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing the spread of speeds between the maximum reverse speeds and the maximum forward speeds of the embodiment.

Provided herein is a vehicle driveline comprising an engine, a variable transmission of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein, and a vehicle output. In some embodiments, the vehicle output comprises a wheel differential and one or more wheels of a vehicle. In some embodiments, the vehicle output comprises a wheel differential and a drive axle. In some embodiments, the dampener is disposed between the engine and the variable transmission. In some embodiments, the dampener comprises at least one torsional spring.

Provided herein is method comprising providing a variable transmission of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein.

Provided herein is a method comprising providing a vehicle driveline of any of configuration described herein or obvious to one of skill in the art upon reading the disclosure herein.

EXAMPLE 1

An exemplary embodiment of the invention is shown in FIG. 4A comprising CVT 3 a. FIG. 4A shows CVT 3 a which may be disposed within a driveline of a vehicle. The driveline may comprise a motor such as an internal combustion engine (ICE) 100, which may be connected to CVT 3 a via an input shaft 1 a, and may optionally feature a clutch and or damper 2 drivingly engaged therebetween. The output 50 a of CVT 3 a may be drivingly engaged to a vehicle differential and wheels 4. The CVT 3 a of the FIG. 4A embodiment is depicted comprising: an input shaft 1 a; a planetary gear set 5 a drivingly engaged with the input shaft though its planet carrier (also referred to as “planetary carrier assembly”) 8 a; a first brake 16 mechanically coupled to a ring gear 9 a of the planetary gear set; a variator 10 a (as described elsewhere in this application) comprising a variator carrier assembly 13 a, a set of tilting balls 14 a, a first ring assembly 12 a, and a second ring assembly 11 a, the variator carrier assembly is mechanically coupled to the ring gear 9 a of the planetary gear set 5 a; and a second brake 17 may be mechanically coupled to the sun gear 6 a of the planetary gear set and to the first ring assembly 12 a. The second ring assembly 11 a is drivingly engaged with the output 50 a of the CVT. The configuration of FIG. 4A includes a continuously variable mode as well as an infinitely variable mode providing a standstill, reverse, and starting function.

The CVT 3 a of FIG. 4A, comprises a continuously variable mode and an infinitely variable mode. When the first brake 16 is engaged and the second brake 17 is disengaged, the ring gear 9 a of the planetary gear set and the variator carrier assembly 13 a (also referred to as a “variator carrier” or “carrier of the variator”) are held fixed, thereby engaging the continuously variable mode. In such a mode power may pass through the sun gear of the planetary to the first ring assembly thereby allowing a continuously variable mode. The infinitely variable mode is engaged when the second brake 17 is engaged and the first brake 16 is disengaged. When the second brake is engaged and the first brake is disengaged, the first ring assembly 12 a and the sun gear 6 a are held fixed and the variator carrier assembly is driven by the input shaft 1 a through the planet carrier 8 a and ring gear 9 a. Tilting the balls 14 a of variator 10 a will allow the second ring assembly 11 a and CVT output 50 a to steplessly transition from reverse to neutral to forward speeds, thereby achieving an infinitely variable mode of CVT 3 a.

FIG. 5 shows the speed diagram of the planetary concept of FIG. 4A.

The axis of FIG. 5 represents the rotation speed of the variator second ring assembly.

As described above, the continuously variable mode is used by applying the first brake 16, holding fixed the ring 9 a of the planetary gear set 5 a as well as the carrier of the variator balls (variator carrier assembly 13 a). The power passes through the sun 6 a and goes to the variator first ring assembly 12 a. The rotation speed achievable in continuously variable mode can be observed as segment 19 on the speed diagram. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

In an infinitely variable mode, the second brake 17 is applied, holding the sun gear 6 a of the planetary 5 a and the first ring assembly 12 a fixed. The power passes through the ring gear 9 a of the planetary gear set 5 a and goes to the carrier of the variator balls 13 a. This mode provides a reverse function as well as a standstill and a low speed. The achievable rotation speeds in the infinitely variable mode can be observed as segment 20 on the speed diagram. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio. As a reference an example ICE rotation speed is shown at point 22.

A small gap may exist between the speeds ranges 19 and 20 of the continuously variable mode and infinitely variable mode and will force the engine to change its speed in order to allow all the vehicle speed. But as this gap is very small, the user will not feel it, the engine speed will only slightly vary, and this design does not need an additional gearbox to help avoid it, although one may be provided nonetheless in an alternative embodiment. FIG. 4B depicts the embodiment of FIG. 4A with such a gearbox 18 added.

The transition between the continuously variable mode and infinitely variable mode is done by simultaneously releasing one of the first brake 16 and the second brake 17, and applying the other one. This embodiment is able to change continuously its ratio in the continuously variable mode and infinitely variable mode to provide the best ratio achievable for the engine in function of the objectives of performance or fuel consumption. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift the ratio. Thereby, in the embodiment of FIG. 4A, the only interruptions of power in this device are the shifting of modes. An additional advantage of this configuration is that a small variator can be chosen.

In some embodiments (FIG. 4B), a gearbox is added so that the gap previously present might be completely covered without engine speed adjustment. The gearbox allows to continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the CVT, the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing the spread of speeds between the maximum reverse speed and the maximum forward speed of the embodiment.

EXAMPLE 2

Provided herein is an embodiment as shown in FIG. 6 comprising a planetary gear set and two brakes to hold either the carrier or the sun fixed. Such an exemplary embodiment of the invention is shown in FIG. 6 comprising CVT 3 b. FIG. 6 shows CVT 3 b which may be disposed within a driveline of a vehicle. The driveline may comprise a motor such as an ICE 100, which may be connected to CVT 3 b via an input shaft 1 b, and may optionally feature a clutch and or damper 2 drivingly engaged therebetween. As in the other embodiments the output 50 b of CVT 3 b may be drivingly engaged to a vehicle differential and wheels 4. The CVT 3 b of the FIG. 6 embodiment is depicted as comprising: an input shaft 1 b; a variator 10 b comprising a first ring assembly 11 b, a second ring assembly 12 b, a variator carrier assembly 13 b, and a set of tilting balls 14 b; a planetary gear set 5 b comprising a ring gear 9 b, sun gear 6 b, planets 7 b and a planetary carrier assembly 8 b; a first brake 16; a second brake 17; and a CVT output 50 b. The configuration of FIG. 6 includes a continuously variable mode as well as an infinitely variable mode providing a standstill, reverse, and starting function.

In the embodiment of FIG. 6, the motor 100 is connected to the ring gear 9 b of the planetary gear set 5 b via input shaft 1 b. The sun gear 6 b of the gear set is connected to a second brake 17 and to the variator carrier assembly 13 b. The planetary carrier 8 b of the planetary gear set is linked to the first ring assembly 11 b of the variator 10 b and can be held fixed by a first brake 16. The second ring assembly 12 b of the variator 10 b is drivingly engaged to the differential (and wheels) 4 of the vehicle through CVT output 50 b. This may be achieved using a series of gears as shown in FIG. 6 or in another manner.

FIG. 7 shows the speed diagram of the configuration shown in FIG. 6.

The axis of FIG. 7 represents the rotation speed of the variator second ring assembly.

In the embodiment of FIG. 6, the continuously variable mode is used by applying the second brake 17, holding fixed the sun 6 b of the planetary gear set as well as the carrier of the variator 13 b. The power passes through the ring 9 b and goes to the first ring assembly 11 b. The rotation speed achievable in continuously variable mode can be observed as segment 25 on the speed diagram. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

In infinitely variable mode of embodiment of FIG. 6, the first brake 16 is applied, holding the carrier of the planetary and the first ring assembly fixed. The power passes through the sun 6 b of the planetary gear set 5 b and goes to the variator carrier 13 b. The power drives variator carrier 13 b while the first ring assembly 11 b remains stationary. As in the embodiment of FIG. 5, tilting the balls 14 b allows the second ring assembly to steplessly transition from reverse, neutral, and forward speeds. Thus an infinitely variable mode is achieved. This mode provides a reverse function as well as a standstill and a low speed. It can be observed as segment 26 on the speed diagram of FIG. 7. An example motor speed 22 is shown as a reference. The overall ratio in the infinitely variable mode is the product of the planetary ratio, the variator ratio and the final drive ratio.

The transition between the two modes as embodied in FIG. 6 is done by simultaneously releasing one of the first and second brakes and applying the other of the first and second brakes. This device is able to change continuously its ratio to provide the best ratio achievable for the engine in function of the objectives of performance or fuel consumption. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. The only interruptions of power in this device are the modes shifting.

EXAMPLE 3

Provide herein is a configuration of a variable transmission and driveline that uses a planetary gear set and two brakes to hold either the ring or the carrier fixed as shown in FIG. 8. Such an exemplary embodiment of the invention is shown in FIG. 8 comprising CVT 3 c. FIG. 8 shows CVT 3 c which may be disposed within a driveline of a vehicle. The driveline may comprise a motor such as an ICE 100, which may be connected to CVT 3 c via an input shaft 1 c, and may optionally feature a clutch and or damper 2 drivingly engaged therebetween. The output 50 c of CVT 3 c may be drivingly engaged to a vehicle differential and wheels 4. The CVT 3 c of the FIG. 8 embodiment is depicted as comprising: an input shaft 1 c; a variator 10 c, comprising a first ring assembly 12 c, a second ring assembly 11 c, a variator carrier assembly 13 c, and a set of tilting balls 14 c; a planetary gear set 5 c comprising a ring gear 9 c, sun gear 6 c, planets 7 c and a planetary carrier assembly 8 c; a first brake 28; a second brake 27; and the CVT output 50 c. The configuration of FIG. 6 includes a continuously variable mode as well as an infinitely variable mode providing a standstill, reverse, and starting function. The central part of that configuration is the variator 10 c, the operation of which is described previously in the document. A ball ramp 15 c on each side of the variator 10 c provides the clamping force necessary to transfer the torque. Having two brakes, this configuration includes a continuously variable mode as well as an infinitely variable mode providing a standstill, reverse and starting function. No starting device like a slipping clutch or torque converter is required, since the infinitely variable mode takes care of the starting function.

The motor 100 is connected to the sun 6 c of the planetary gear set 5 c. The planetary carrier 8 c connected to the second brake 27 and then to the first ring assembly 12 c. The ring 9 c of the planetary gear set is linked to the carrier of the variator and can be held fixed by first brake 28.

FIG. 9 shows the speed diagram of that configuration.

The axis represents the rotation speed of the variator second ring assembly.

As depicted in FIG. 8 a continuously variable mode is used by applying the first brake 28, holding fixed the ring 9 c of the planetary gear set as well as the variator carrier 13 c. The power passes through the planetary carrier 8 c and goes to the first ring assembly 12 c. The rotation speed achievable in CVP mode can be observed as segment 30 on the speed diagram. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

In infinitely variable mode, the second brake 27 is applied, holding the carrier of the planetary gear set 8 c and the first ring assembly 12 c fixed. The power passes through the ring 9 c of the planetary gear set 5 c and goes to the carrier of the variator. In the same manner of the embodiments of FIGS. 4A and 6 this power flow allows for the second ring assembly 11 c to steplessly transition between reverse, neutral and forward speeds, thereby achieving an infinitely variable mode at the CVT 3 c output 50 c. This mode provides a reverse function as well as a standstill and a low speed. It can be observed as segment 31 on the speed diagram. An example motor speed 32 is shown as a reference. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

The transition between the two modes as embodied in FIG. 8 is done by simultaneously releasing one of the first and second brakes and applying the other of the first and second brakes. This device is able to change continuously its ratio to provide the best ratio achievable for the engine in function of the objectives of performance or fuel consumption. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. The only interruptions of power in this device are the modes shifting.

EXAMPLE 4

An exemplary embodiment of the invention is shown in FIG. 10 comprising CVT 3 d. FIG. 8 shows CVT 3 d which may be disposed within a driveline of a vehicle. The driveline may comprise a motor such as an ICE 100, which may be connected to CVT 3 d via an input shaft 1 d, and may optionally feature a clutch and or damper 2 drivingly engaged therebetween. The output 50 d of CVT 3 d may be drivingly engaged to a vehicle differential and wheels 4. The CVT 3 d of the FIG. 10 embodiment is depicted as comprising: an input shaft 1 d; a variator 10 d, comprising a first ring assembly 11 d, a second ring assembly 12 d, a variator carrier assembly 13 d, and a set of tilting balls 14 d; a planetary gear set 5 d comprising a ring gear 9 d, sun gear 6 d, planets 7 d and a planetary carrier assembly 8 d; a first brake 33; a second brake 34; and the CVT output 50 d. As in the other embodiments the CVT output 50 d may be coupled to a vehicle differential and wheels (not shown). This configuration uses a planetary gear set and two brakes to hold either the planetary ring gear 9 d or the variator carrier 13 d fixed. The central part of this configuration is the variator 10 d (such variators are described previously in the document). A ball ramp 15 d on each side of the variator provides the clamping force necessary to transfer the torque. Having two brakes, this configuration includes a continuously variable mode as well as an infinitely variable mode providing a standstill, reverse and starting function. No starting device like a slipping clutch or torque converter is required, since the infinitely variable mode takes care of the starting function.

The motor 100 (for example an internal combustion engine) is connected to the 6 d of the planetary gear set via input shaft 1 d. The ring 9 d of the planetary gear set is connected to the first brake 33 and to the first ring assembly 11 d. The planetary carrier assembly 8 d is linked to the carrier of the variator 10 d and can be held fixed by the second brake 34.

FIG. 11 shows the speed diagram of that configuration.

The axis represents the rotation speed of the variator second ring assembly.

Continuously variable mode is used by applying the second brake 34, holding fixed the planetary carrier 8 d as well as the variator carrier assembly 13 d. The power passes through the ring gear 9 d and goes to the first ring assembly 11 d and through the variator 10 d thereby engaging the continuously variable mode. The rotation speed achievable in continuously variable mode can be observed as segment 35 on the speed diagram. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

In infinitely variable mode, the first brake 33 is applied, holding the ring gear 9 d of the planetary gear set and the first ring assembly 11 d fixed. The power passes through the planetary carrier 8 d and goes to the variator carrier assembly 13 d. As in the embodiments of FIGS. 4A, 6 and 8 this thereby allows an infinitely variable mode. This mode provides a reverse function as well as a standstill and a low speed. It can be observed as segment 36 on the speed diagram of FIG. 11. An example motor speed 37 is shown as a reference. The overall ratio is the product of the planetary ratio, the variator ratio and the final drive ratio.

The transition between the two modes as embodied in FIG. 10 is done by simultaneously releasing one of the first and second brakes and applying the other of the first and second brakes. This device is able to change continuously its ratio to provide the best ratio achievable for the engine in function of the objectives of performance or fuel consumption. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. The only interruptions of power in this device are the modes shifting.

EXAMPLE 5

An exemplary embodiment of the invention is shown in FIG. 12 comprising CVT 3 e. FIG. 10 shows CVT 3 e which may be disposed within a driveline of a vehicle. The driveline may comprise a motor such as an ICE 100, which may be connected to CVT 3 e via an input shaft le, and may optionally feature a clutch and/or damper 2 drivingly engaged therebetween. The output 50 e of CVT 3 e may be drivingly engaged to a vehicle differential and wheels 4. The CVT 3 e of the FIG. 12 embodiment is depicted as comprising: an input shaft 1 e; a variator 10 e, comprising a first ring assembly 11 e, a second ring assembly 12 e, a variator carrier assembly 13 e, and a set of tilting balls 14 e; a planetary gear set 5 e comprising a ring gear 9 e, sun gear 6 e, planets 7 e and a planetary carrier assembly 8 e; a first brake 38; a first clutch 39; and the CVT output 50 e. The transmission configuration depicted in FIG. 12A uses a planetary gear set, one brake and one clutch. The central part of that configuration is the variator 10 e described previously herein. A ball ramp 15 e on each side of the variator 10 e provides the clamping force necessary to transfer the torque. This configuration includes a continuously variable/infinitely variable mode as well as an infinitely variable mode providing a standstill, reverse and starting function. No starting device like a slipping clutch or torque converter is required, since the infinitely variable mode takes care of the starting function.

The motor 100, for example an internal combustion engine, is connected to the sun 6 e of the planetary gear set 5 e. The planetary carrier assembly 8 e is connected to the variator carrier assembly 13 e while the ring 9 e of the planetary gear set 5 e is always held fixed. The first ring assembly can be held by the brake 38 or connected to the engine by the clutch 39.

FIG. 13 shows the speed diagram of the configuration of FIG. 12A.

The axis represents the rotation speed of the variator second ring assembly.

The infinitely variable/continuously variable mode is used by engaging the clutch 39, connecting the engine to the first ring assembly 11 e, thus letting the first ring assembly and variator carrier be both driven. This infinitely variable/continuously variable mode lies in between the infinitely variable mode and the continuously variable mode concerning speeds. The overall ratio is the product of the sun planetary ratio, the variator ratio and the final drive ratio. The rotation speed achievable in infinitely variable/continuously variable mode can be observed as segment 41 on the speed diagram.

In infinitely variable mode, the brake 38 is applied, holding the first ring assembly 11 e while the clutch 38 is disengaged. The power passes through the planetary carrier assembly 8 e and goes to the variator carrier assembly 13 e. As in previously described embodiments driving the variator carrier assembly 13 e while holding the first ring assembly 11 e allows stepless transitions of the second ring assembly 12 e between positive negative and neutral speeds, thereby accomplishing a infinitely variable mode. This mode provides a reverse function as well as a standstill and a low speed. It can be observed as segment 42 on the speed diagram. The overall ratio is the product of the sun planetary ratio, the variator ratio and the final drive ratio.

A gap exists between the infinitely variable mode and infinitely variable/continuously variable mode and will be covered by changing the engine speed in order to allow all the vehicle speed.

The transition between the two modes is done by releasing a clutch end engaging the brake to go from the infinitely variable/continuously variable mode to the infinitely variable mode. This device is able to change continuously its ratio in the infinitely variable and infinitely variable/continuously variable modes to provide the best ratio achievable for the engine in function of the objectives of performance or fuel consumption. In a manual or automatic transmission, only some predetermined and discrete ratios are available and an interruption of the power transmission is needed to shift of ratio. The only interruptions of power in this device are the modes shifting. An additional advantage of that configuration is that a small variator can be chosen.

FIG. 12B depicts the embodiment of FIG. 12A with a gearbox 40 mechanically coupling the CVT output 50 e to the differential 4. The gearbox added so that the gap previously present might be completely covered without engine speed adjustment. The gearbox allows to continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio in the CVT, the clutches engaged, and the gearbox ratio. Such a gearbox might also allow increasing the spread of speeds between the maximum reverse speed and the maximum forward speed of the embodiment.

Embodiments of the variable transmission described herein or that would be obvious to one of skill in the art upon reading the disclosure herein are contemplated for use in a variety of vehicle drivelines. For non-limiting example, the variable transmissions disclosed herein may be used in bicycles, mopeds, scooters, motorcycles, automobiles, electric automobiles, trucks, sport utility vehicles (SUV's), lawn mowers, tractors, harvesters, agricultural machinery, all terrain vehicles (ATV's), jet skis, personal watercraft vehicles, airplanes, trains, helicopters, buses, forklifts, golf carts, motorships, steam powered ships, submarines, space craft, or other vehicles that employ a transmission.

While the figures and description herein are directed to ball-type variators (CVTs), alternate embodiments are contemplated another version of a variator (CVT), such as a Variable-diameter pulley (VDP) or Reeves drive, a toroidal or roller-based CVT (Extroid CVT), a Magnetic CVT or mCVT, Ratcheting CVT, Hydrostatic CVTs, Naudic Incremental CVT (iCVT), Cone CVTs, Radial roller CVT, Planetary CVT, or any other version CVT.

While preferred embodiments of the present invention have been shown and described herein, it will be obvious to those skilled in the art that such embodiments are provided by way of example only. Numerous variations, changes, and substitutions will now occur to those skilled in the art without departing from the invention. It should be understood that various alternatives to the embodiments of the invention described herein may be employed in practicing the invention. It is intended that the following claims define the scope of the invention and that methods and structures within the scope of these claims and their equivalents be covered thereby. 

What is claimed is:
 1. A variable transmission comprising: an input shaft; a planetary gear set drivingly engaged with the input shaft; a first brake mechanically coupled to an outer ring gear of the planetary gear set; a variator comprising a variator carrier assembly, a first ring assembly, and a second ring assembly, the variator mechanically coupled to a ring gear of the planetary gear set; a second brake mechanically coupled to a sun gear of the planetary gear set and to a first ring assembly of the variator; and the second ring assembly of the variator drivingly engaged to a gearbox; wherein the gearbox is drivingly engaged to an output of the variable transmission.
 2. The variable transmission of claim 1, comprising a continuously variable mode and an infinitely variable mode.
 3. The variable transmission of claim 1, wherein when the first brake is engaged and the second brake is disengaged, the ring gear of the planetary gear set and the carrier of the variator are held fixed, thereby engaging a continuously variable mode.
 4. The variable transmission of claim 2, wherein power passes through the sun gear of the planetary gear set to the first ring assembly when the transmission is in the continuously variable mode.
 5. The variable transmission of claim 1, wherein when the second brake is engaged and the first brake is disengaged, the sun gear of the planetary gear set and the first ring assembly are held fixed, thereby engaging an infinitely variable mode.
 6. The variable transmission of claim 5, wherein power passes through the ring gear of the planetary gear set to a carrier of the variator in the infinitely variable mode.
 7. The variable transmission of claim 2, wherein in the infinitely variable mode, the variator provides a reverse function, a standstill function and a low speed function.
 8. The variable transmission of claim 2, wherein a transition between continuously variable mode and infinitely variable mode is accomplished by simultaneously releasing one of the first brake and the second brake while applying the other of the first brake and the second brake.
 9. The variable transmission of claim 2, wherein the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption.
 10. The variable transmission of claim 2, wherein the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.
 11. The variable transmission of claim 3, wherein the continuously variable mode provides a gap in rotation speeds of the second ring assembly, wherein the gap is capable of being compensated without engine speed adjustment by continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio at the variator, the clutches engaged, and the gearbox ratio.
 12. The variable transmission of claim 3, wherein the gearbox allows for an increase in a spread between the maximum reverse speed and the maximum forward speed of the variable transmission output.
 13. The variable transmission of claim 1, comprising a continuously variable/infinitely variable mode and the infinitely variable mode.
 14. The variable transmission of claim 13, wherein the clutch is engaged/disengaged and the first brake is engaged/disengaged.
 15. The variable transmission of claim 13, wherein continuously variable/infinitely variable mode and the infinitely variable mode provide a gap in rotation speeds of the second ring assembly, wherein the gap is capable of being compensated without engine speed adjustment by continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio at the variator, the clutches engaged, and the gearbox ratio.
 16. The variable transmission of claim 15, wherein the gearbox allows for an increase in a spread between the maximum reverse speed and the maximum forward speed of the variable transmission output.
 17. A variable transmission comprising: an input shaft; a clutch comprising a first clutch member coupled to the input shaft and a second clutch member; a variator comprising a first ring assembly having the second clutch member formed thereon, a second ring assembly drivingly engaged to an output of the variable transmission, and a carrier assembly; a planetary gear set comprising a sun gear drivingly engaged with the input shaft, one or more planet gears on a planet carrier that is drivingly engaged with a variator carrier of the carrier assembly, wherein a ring gear of the planetary gear set is held fixed; a first brake coupled to the first ring assembly configured to hold the first ring assembly fixed when the first brake is engaged, wherein the first ring assembly is drivingly engaged with the input shaft when the first clutch member engages the second clutch member, and the second ring assembly of the variator is drivingly engaged to a gearbox; wherein the gearbox is drivingly engaged to an output of the variable transmission.
 18. The variable transmission of claim 17, comprising a combined continuously variable/infinitely variable mode, or an infinitely variable mode.
 19. The variable transmission of claim 18, wherein when the clutch is engaged, both the first ring assembly and the variator carrier are driven in order to engage the combined continuously variable/infinitely variable mode.
 20. The variable transmission of claim 18, wherein the variable transmission in the combined continuously variable/infinitely variable mode generates rotation speeds of the second ring assembly between speeds generated in a continuously variable mode and a infinitely variable mode.
 21. The variable transmission of claim 18, wherein when the first ring assembly is held fixed with the brake and the clutch is disengaged, the infinitely variable mode is engaged.
 22. The variable transmission of claim 21, wherein the power passes through the planet carrier of and to the variator carrier in the infinitely variable mode.
 23. The variable transmission of claim 18, wherein the variator provides a reverse function, a standstill function and a low speed function in the infinitely variable mode.
 24. The variable transmission of claim 18, wherein a transition between the continuously variable/infinitely variable mode and the infinitely variable mode is accomplished by disengaging the clutch and engaging the brake.
 25. The variable transmission of claim 18, wherein the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to optimize performance or fuel consumption.
 26. The variable transmission of claim 18, wherein the variator continuously changes its torque ratios in both the continuously variable mode and infinitely variable mode to achieve an ideal ratio for variable transmission.
 27. The variable transmission of claim 18, wherein the continuously variable/infinitely variable mode and infinitely variable mode provide a gap in rotation speeds of the second ring assembly, wherein the gap is capable of being compensated by the gearbox.
 28. The variable transmission of claim 17, wherein the gearbox allows for an increase in a spread between the maximum reverse speed and the maximum forward speed of the variable transmission output.
 29. The variable transmission of claim 18, wherein continuously variable/infinitely variable mode and the infinitely variable mode provide a gap in rotation speeds of the second ring assembly, wherein the gap is capable of being compensated without engine speed adjustment by continuously varying the speed from the max reverse speed to the max forward speed by appropriately selecting the ratio at the variator, the clutches engaged, and the gearbox ratio.
 30. The variable transmission of claim 29, wherein the gearbox allows for an increase in a spread between the maximum reverse speed and the maximum forward speed of the variable transmission output. 